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NOZZLE 6 Sheets-Sheet l Allg- 7, 1956 J. F. CAMPBELL.

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Aug. 7, 1956 J. F. CAMPBEPL 2,757,968

NOZZLE Filed Aug. 23, 1954 6 Sheets-Sheet 6 INVENTOR. l0/IN f GQMPEELL Afrom/575.

United States Patent AUTOMAHC nmBoN `REWIND CUT-oFF Vincent J. Gilmore,Wappingcrs Falls, N. Y., assignor to International Business MachinesCorporation, New York, N. Y., a corporation of New York Application July30, 1953, Serial No. 371,331

` s claims. (cl. A197.--151) This invention relates to typewritingmachines, and more particularly to an improved ribbon winding mechanismfor such machines.

When the ribbon of a typewriter becomes worn and needs to be replaced bya new ribbon, it is `necessary that the operator either manually rotatethe ribbon spool which has the most ribbon wound thereon until theremaining spool is exhausted, or make use of some mcchanical rewindingmechanism.

The Hazleton Patent 2,540,031 discloses a ribbon rewinding mechanismwhich operates continuously as long as a rewind key is held depressed.As soon as the ribbon is completely wound on one spool, the mechanismautomatically reverses the winding operation if the 4key kis helddepressed. With the Hazleton device, the operator must visuallydetermine when the ribbon is wholly wound on one spool. At this point,the operator must release the key before the reversing mechanismoperates to wind the ribbon back on the empty spool.

The manual rotation of the ribbon spool is slow, tedious, and very aptto soil the hands of the operator. The mechanism disclosed by Hazletonis vfaster but requires the careful and continuous attention of theoperator.

A broad object of the present invention is to provide an improved ribbonwinding mechanism.

Another object of the invention is to provide an improved ribbonrewinding mechanism which operates by the depression of a key to rewindthe ribbon on one or the other of two spools.

Yet another object is to provide an improved power operated ribbonwinding mechanism which ,operates continuously, upon the depression of akey, until all the ribbon is `wound on one or the other of two ribbonspools and then stops automatically.

Other objects of the invention will be pointed vout in the followingdescription and claims and illustrated in the accompanying drawings,which disclose by way of eX8-.II1P1e, the principle of the invention andthe best mode which has been contemplated of vapplying that principle.

In the drawings:

Fig. 1 is a sectional view of a typewriter showing a single type bar andits actuating mechanism.

Fig. 2 is a side elevational view of the improved ribbon winding devicein its normal inoperative position.

Fig. 3 is an enlarged view of mechanism partially lshown in Fig. 2 foractuating a power unit to effect stepby-step winding of the ribbon.

Fig. 4 is a .detail view of certain parts of the winding mechanism shownyin Fig. 2.

Figs. 5 and 6 are views similar t0 Fig. 4 but showins parts in differentpositionsln Fig. 1 is shown a vertical sectionV of a power operatedtypewriter in which keys 1 are pivoted on a cross rod 2 and guided attheir front ends by a suitable-key cfmib 3, 1th,@ .keys being restoredby .Springs 4. The keys 1 .control Power mechanisms which are driven by:a power relier 6 normally rotating .countrclockwise as .in

2,757,776 Patented Aug. 7, 1956 Fig. l. Each key controls its own powerunit, all of which coact with the power roller 6 to operate thecorresponding type bars 7.

Each power unit includes a lever 8 which is pivoted by means of a notch9 on an individual fulcrum bar il mounted on a support bar 12. Thelevers 8 are held in engagement with the bars 11 by springs 13 anchoredto suitable lugs on the bars 11. The upper end of each lever 8 isconnected by a link 14 to an arm 16 on the associated type bar 7 whichis pivotally mounted at a point 17.

Each power unit also includes an L-shaped lever i8 pivoted at 19 on thelever 8 and urged in a counterclockwise direction by a spring 21anchored to an ear formed on the lever. An interposer 22 having an upperlug 23 and a lower lug 24 is pivotally mounted at 26 on the lever 8 andis urged in a clockwise direction by a spring 27. The depression of thekey 1 causes an extension 23 of the lever 1 to engage the lug 23 androck the interposer 22 in a counterclockwise direction. The lug 24 thenforces the lever 18 in a clockwise direction and causes the serratedtread portion 29 of the cam to engage the power roller 6 and be grippedthereby. Rotation of the power roller causes the cam 18 to swing aboutits pivot 19, and due to the eccentricity of the cam tread 29 withrespect to the pivot 19, eiect a rocking of the lever 8 in a clockwisedirection about the pivot 9, against the tension of the spring 13thereby actuating the type bar 7 to printing position.

Pivotally mounted on the framework of the machine is a cross shaft 31 onwhich is pivotally `mounted a universal bar or bail 32. This bail 32 isengaged by the nose piece 33 of the lever 8 whereby each time the leveris operated, the bail 32 is actuated in a counterclockwise direction.This movement of the bail 32 is utilized to trip a power unit in amanner to be explained.

Referring to Fig. 2, suitably supported in the machine framework by aXed frame piece 36 is a power unit generally designated 37. The powerunit 37 includes a suitable frame 38 pivoted at 39 on the frame 36. Anelliptical cam 41 is pivoted at 42 in the frame 38, and the cam 41 isprovided with two pins 43 located on diametrically opposite sides of thepivot 42. One of the pins 43 is normally engaged by an arm 44 pivoted at46 in the frame 38. This arm 44 is urged in a clockwise direction by atorsion spring 47 partly coiled around the pivot 46 and hooked to lugsformed in the ann 44 and in the yframe 38.

Also pivoted at 46 is a trip lever 43 having an offset lug 49 coactingwith one of two pins 51 set in the cam 41 on diametrically oppositesides of the pivot 42 to limit rotation of the cam 41. Thespringactuated lever 44 pressing on one of the pins 43 tends to rotate the cam41 in a clockwise direction about its pivot point 42. In this positionof the parts, there is a small clearance between the tread of the cam 41and an enlarged portion 52 formed on or suitably secured to thecontinuously running power roller 6.

When the trip lever 48 is pivoted in a clockwise direction about thepivot 46 by means to be disclosed, the lug 49 is moved upwardly out ofthe path of the pins 5,1 and the cam 4 1 is rotated slightly clockwiseby action of the spring tensioned lever 44 on one of the pins 43. Thisslight clockwise rotation brings a high portion of the cam 41 intocontact with the portion 52 of the power roller 6, causing clockwiserotation of the cam 41 about pivot 42.

The trip lever 48 may be rocked in a clockwise direction by two diierentmeans to actuate the pOWel' unit 37. Referring to Fig. 3, the iirstmeans is the above described individual type bar power units. When thenose piece 33 of theS lever 8 engages the bail 32 and rotates itin acounter-clockwise direction, the bail engages an arm S3 (Fig. 3),pivoted on the end of the cross shaft 31, and rotates it in acounterclockwise direction about the shaft 31, thereby shiftingdownwardly a link 54 joining the arm 53 and the actuating lever 48. Thedownward movement of the link 54 rotates the lever 48 in a clockwisedirection and disengages the lug 49 from the pin 51. At the same time, alug 56 also formed in the trip lever 48, is positioned in the path ofmovement of the second pin 51 so as to allow only one-half revolution ofthe cam 41. The trip lever 48 is then rocked in a counterclockwisedirection by a spring 57 anchored to the frame 3S und to a lug carriedby the trip lever 48. The lug 56 slips off the pin 51 but the pin 51 isthen immediately engaged by the lug 49 and further rotation isprevented.

The second means for actuating the power unit 37 utilizes a member 58.Referring to Figs. 2 and 5, the member 58 is supported for verticalsliding movement by means of two slots 59 and 61 engaging studs 62 and63 which are rigidly mounted in a frame plate adjacent the power unit37. The member 58 is held in its normal,

raised position, Figs. 2 and 4, by a spring 67 tensioned between theframe stud 63 and a lug 68. The member 58 may be manually depressed to aposition in which a notch 69 at one end of the slot 61 lies adjacent thestud 63. At this time, the member is pivoted by the spring 67 about thestud 62 to engage the notch 69 with the stud 63 for holding the memberdepressed. With the member in this depressed position, its lower end 71acts against a pin 72 on the lever 48 for holding the latter in such aposition that both the lugs 49 and 56 on the lever 48 are raised out ofthe path of the pins 51 and leave the cam 41 free to rotatecontinuously.

With the rotation limiting lug 49 and the repeat preventing lug 56 outof the path of the pins 51, the cam 41 contacts the roller portion 52and rotates in a clockwise direction continuously until the trip lever48 is allowed to rock in a counterclockwise direction under the tensionof the spring 57, again placing the lug 49 in the path of the pins 51.

Due to the eccentricity of the lobes on the cam 41 and the action of aspring 73 connecting the frame 38 to a lng 74 on the xed frame 36, anoscillating motion is imparted to the frame 38. Fixed to the frame 36 isa resilient bumper 76 for limiting the counterclockwise rocking movementof the frame 38.

Referring to Fig. 2, the cross shaft 31 is provided at its opposite endswith two arms 77, the left one of which is connected by a link 78 to thepivoted frame 38. The shaft 3l. is rocked in synchronism with theoscillation of the frame 38 through the connecting link 78 and left arm77. Attached to each of the arms 77 is a link 79 which actuates a ribbonmechanism associated with a ribbon spool. Fig. 2 shows the ribbonfeeding mechanism located on the left hand side of the machine, but itwill be understood that the two mechanisms are similar in constructionand the description of one will suffice for both. The side plate 81 ofthe main framework is formed with a large open, cut-out portion 82 t'oaccommodate the ribbon mechanisms. Each of these mechanisms has a spool83 and various control means mounted as a unit in the cutout 82 of theassociated side frame 81, by means of a plate 84 attached by threescrews 86.

The link 79 for the left hand spool 83 is connected to one arm of alever 87 which is pivoted on a stud 88 carried by the plate 84. Anotherarm of the lever 87 has pivoted at 89 a feed pawl 91 which is urged in aclockwise direction by a spring 92 to engage the usual ratchet teeth 94of the ribbon spool 83 when the ribbon feed mech-k anism is in conditionto feed the ribbon onto the left hand spool.

When the power unit 37 is rendered operative in the manner describedabove to impart an oscillating movement to the shaft 31, both links 79are oscillated up and down. This movement of the links 79 will cause thelever 87 associated with the pawl 91 to be actuated in a clockwisedirection and, if the pawl 91 is engaged with the teeth 94, the spool 83will be rotated in a clockwise direction. It will be understood that thelevers 87 for both feeding mechanisms will be oscillated each time thelinks 79 are oscillated, but the driving of a ribbon spool depends uponwhether or not the pawl 91 for that particular spool is engaged with theratchet teeth.

A mechanism is provided for causing the pawls 91 to engage the teeth 94of the ribbon spools in alternation so as to cause one ribbon spool tofeed until the other is exhausted and then to automatically render theother spool effective to feed. This mechanism is controlled by thetension produced in the ribbon when the free-running spool is exhausted.Pivoted at 96 on a plate 97, which is shaped somewhat like a letter Greversed right to left, is an interposer 98 which is connected by a link99 to one arm of a tension lever 101 pivoted at 102 on the plate 84. Thetension lever 101 is formed with a ribbon guide lug 103 having an openribbon guiding slot formed therein and is urged in a clockwise directionagainst a stop lug 104 by a spring 106. Due to the fact that the ribbonis secured to the spools, sufficient tension will be built up in theribbon when a spool is exhausted to cause the tension control lever 101of the free-running spool to pivot in a counterclockwise direction,while the tension control lever of the driven spool is unaffected. Whenall the ribbon has been wound onto one of the spools, the angles betweenthe ribbon on the full spool and the lever 101 are such that an increasein tension on the ribbon has no tendency to swing the lever about itspivot. The ribbon at the empty spool, however, extends from theassociated lever at such angles that an increase in the tension on theribbon causes the lever to swing. Through the link connection 99, theinterposer 98 will be rotated in a clockwise direction by the movementof the control lever 101 and into the path of an offset lug 107 formedon the lever 87 Consequently, the next oscillation of the lever 87 bythe link 79 will cause the plate 97 of the free-running spool mechanismto be shifted upwardly rendering the pawl 91 effective to drive thepreviously free-running ribbon spool 83 With each clockwise oscillationof the lever 87. The plate 97 is formed with a long offset lug 108, likethe cross bar of a G, disposed between the pawl 91 and the teeth 94 sothat with the plate 97 in the lower position, Figs. 4 and 6, the pawl 91is prevented from engaging the teeth 94, but when the plate 97 isshifted upwardly as in Figs. 2 and 5, the pawl 91 will be permitted toengage the teeth 94.

A manual means also is provided for controlling the driving of thespools so as to obtain a winding of the ribbon onto the spool containingthe greater portion of the ribbon. Pivotally connected to the left handmember 97 at 109 and to the frame piece 84 at 111 is a manual lever 112,the operation of which will disengage the feed pawl 91 from the teeth 94of one spool and engage the other feed pawl with the teeth of the otherspool.

' (not shown) similarly has a loose pin connection 117 with a lever 118disposed on the right end of the cross shaft 116 adjacent the plate 97for the right hand spool feeding mechanism so that the pins 113 and 117are approximately 180 apart with respect to the cross shaft 116. Whenthe left hand plate 97 is shifted upwardly, as in Figs. 2 and 5, toengage the left hand pawl 91 with the ratchet teeth 94 of the left handribbon spool 83, the cross shaft 116 is rotated in a clockwise directionby means of the pin 113 and the lever 114 to shift the right hand plate97 downwardly by means of the lever 118 and the pin 117. This disengagesthe right hand pawl 91 from the ratchet teeth 94 of the right hand spool83 and renders the right hand spool free-running.

In order to hold the plates 97 in their alternate shifted positions, thelever 118 is provided with an arm 119 which is engaged by one branch ofa toggle spring 121,

arcanes justing screw 32 in conjunction with the thickness of a selectedwasher or shim 74 will determine the fluid pressure required thus toreciprocate valve member 14 to admit fluid pressure past such bevelledcontour. Of course, the opposed surface of bore 13 may be contoured inthe regions adjacent such inlet ports to determine the change in rate offluid flow as the valve member is reciprocated instead of bevellingvalve member 14 as shown, or both may be contoured.

The operation of my nozzle may now be understood, being generallysimilar to that described in my aforesaid Patent No. 2,656,218 and mytro-pending application Serial No. 333,569. Fluid such as liquid fuelenters the nozzle from the fuel manifold and is discharged through exitorice 12 into a relatively low pressure exterior chamber. Since inletports 18, 19 and 20 are ordinarily always open, uid pressure in inlet 11is exerted both against the end of valve member 14 and also against theinner surface of vtappet valve member 27 and when such pressure reachesa sufficient point as determined by preset compression spring 34, suchvalve members 14 and 27 will be shifted in unison to open exit orifice12. The fluid from channels 15, 16 and 17 passes through helical swirlgrooves 24 to enter swirl chamber 26 and pass through the exit orificein the form of a spray cone. Such spray cone is formed even when exitvalve member 27 is only very slightly opened inasmuch as inlet ports 18,19 and Ztl are nevertheless normally wide Iopen and thereby admitsubstantial lluid pressure to chamber 26.

When the uid pressure bearing against valve member 14 is effective toshift the same to uncover annular inlet port 42, additional fluid flowis now admitted to the remaining helical grooves 24 and delivered toswirl chamber' 26. lt will be appreciated that the fluid pressurebearing against the end of valve member 14 is principally effective incontrolling the reciprocation of both valve members (through theintermediary of rod 29) inasmuch as the effective area of exit valvemember 27 subject to fluid pressure thereagainst is much smaller and soof relatively little consequence. The spinning inertia of fuel particlesin the envelope formed at the opening of exit valve 27 causes suchparticles to break away and disintegrate the envelope into a finelyatomized mist which then further disintegrates into a relatively dryvapor.

Constricted helical channels 24 prevent a high fluid pressure fromdeveloping in swirl chamber .26 when the exit valve has been thusinitially rather widely opened, and accordingly the initial fluiddischarge of the nozzle will be at a relatively low rate. Suchconstricted helical channels likewise ensure that substantial intakepressure is maintained against regulator valve member 14.

As the rate of fuel flow is increased, regulator valve member 14 isgradually shifted from left to right as viewed in Figs. l-3 and 10-12,bringing the bevelled shoulder `of the same past the edge of annularinlet port 64 (Fig. l2). Fuel accordingly enters such port to anincreasingT extent as the valve opens and passes therefrom throughchannels 555-63 inclusive and swirl slots 66 to swirl chamber 26 andthence out orifice 12. Exit valve member 27 has, of course, beencorrespondingly opened as regulator valve 14 was opened, due toreciprocation of resilient rod 29 connecting such two valve members.There continues to be a certain amount of fuel flow through channels -17and channels 36-41 and spiral passages 24, but this soon becomesrelatively inconsequential when compared to the very much larger llowentering through port 64 and thence passing through channels 55-63.

The bevel or contour 73 of valve member 14 will ordinarily be selectedso that at maximum rated fuel flow the pressure drop between port 64 andswirl chamber 26 will be as low as possible and still afford sufficientswirling action through slots 66 to provide satisfactory atomization ofthe fuel at the orifice. Such bevelled contour need not necessarily be astraight line and other curves may be employed when suitable. The swirlslots 66 afford a result at higher rates of flow similar to that ofhelical passages 24 at low fuel llow, but the pressure loss throughslots 66 is much less since they are of relatively large cross-section.

lt will be seen from the foregoing that l have provided a fluid pressureresponsive nozzle having a set of normally open ports 18, 19 and 26 incommunication with the swirl chamber immediately upstream of the exitorifice 12 and a plurality (in this case, two) of sequentially valvedports for admitting increased fluid flow to such swirl chamber inresponse to increasing inlet pressure. By this arrangement I havesucceeded in considerably extending the range of fluid flow obtainablewhile maintaining at least the minimum velocity in the swirl chambereffective to afford satisfactory atomization of the fuel passing throughexit on'ce 12. At the same time l avoid the production of too high avelocity ilow through the channels within the nozzle leading to suchswirl chamber. A ratio of maximum flow to minimum flow of 87 to l isreadily obtainable with my new construction while thus affording properswirl chamber velocity both at maximum flow and minimum flow.Consequently, an engine utilizing my new nozzles may be throttled up ordown for precise control without the necessity of cutting additionalnozzles in and out. If desired, eyen more precise control may beobtained by providing additional channels and ports sequentially openedas valve member 14 is recipro-cated.

is best shown in Fig. l, the edges of ports 42 and 64 are very closetogether, and also port 4.2 is very narrow where it enters bore 13,preferably only a few thousandths of an inch wide, so that in case theWire connector rod 29 should fail (with the loss of exit valve member27) the regulator valve member 14 will need to move only a shortdistance under the inluence of the relaxing spring preload in order toclose both ports 64 and 42. Ports 42 and 64 may desirably be spaced onlya few thousandths of an inch apart, the space therebetween preferablynot exceeding eight thousandths of an inch for a common size of jetengine nozzle, and the Width of the opening of port 42 may likewisedesirably not exceed eight thousandths of an inch in such case. Openingmovement of regulating valve member 14 is thus effective to bring intouse the second set of normally closed passages promptly after openingthe lirst set, under influence of fluid intake pressure. Obviously thepassages may be subdivided as convenient if symmetrically arranged toaord a balanced lluid llow. Thus, there is a normally open passage(subdivided into 15, 16 and 17) leading to the swirl chamber through thesmall helical slots 24, a normally closed passage of larger capacity(subdivided into 36-41) also leading to the swirl chamber throughhelical slots 24, and a still larger normally `closed passage adaptedfor subsequent opening by reciprocation of valve member 14 (subdividedinto 55- 63).

Referring now to Fig. 13 of the drawing, another embodiment of myinvention is there illustrated comprising an open orifice form or nozzlegenerally similar to that above described but without provision of anexit orifice valve member. Thus, inner end member 75, preferably havinga reduced neck 76 extending through and slightly beyond the open endorifice 12, serves to close the bore `13 of member 9 except for a smallvent passage 77 leading to the exterior of the nozzle. If desired,member 75 may be formed Without the neck 76, otherwise being similarlyconstructed and operative. The intake end lll of the nozzle willnormally be in communication with the combustion chamber of the engineor other external environment through the open exit orifice 12. The sizeof such orice may be somewhat more restricted than when a tappet valvemember protrudes therethrough. A snap ring 78 may desirably be employedto ensure that valve member 14 does not reciprocate too far to the leftas viewed in Fig. 13. As shown in such figure, spring 34 is compressedso that fluid is escaping through both ports 42 and 64. Shim 74 will beselected, however, so that under normal conditions with minimum intakepressure, valve member 14 will close both such ports but will not closeport 18. There will consequently normally be a very slight escape ofiiuid through exit orifice 12 when the intake end pressure is very low.While this form of nozzle obviously does not include variousadvantageous features of the closed orifice type of nozzle abovedescribed, nevertheless it is capable of delivering a uid spray over abroad range of fiow and will be adequate for some purposes.

Other modes of applying the principle of the invention may be employed,change being made as regards the details described, provided thefeatures stated in any of the following claims or the equivalent of suchbe employed.

I therefore particularly point out and distinctly claim as my invention:

1. In a nozzle having an exit orifice, a swirl chamber of fixeddimensions immediately upstream of such orifice, a small passage leadingfrom the intake end of said nozzle to such orifice, two larger passagesleading from the intake end of said nozzle to such orifice, an exitvalve member normally closing such orifice, a regulating valve memberoperative sequentially to open said two larger passages in response toincrease in fluid intake pressure, said small passage being normallyopen, and means connecting said exit valve member and regulating valvemember for reciprocation in unison, said exit valve member beingarranged upon reciprocation to open such exit orifice before saidregulating valve opens the rst of said larger passages.

2. In a nozzle having an exit orifice, a normally open passage leadingfrom the intake end of said nozzle to such orifice, a plurality ofnormally closed passages leading from the intake end of said nozzle tosuch orifice, an exit valve member normally closing such orificeexternally thereof, a regulating valve member operative sequentially toopen said normally closed passages in response to increase in uid intakepressure, and means connecting said exit valve member and regulatingvalve member for reciprocation in unison, said exit valve member beingarranged upon reciprocation to open such exit orifice before saidregulating valve opens the first of said normally closed passages.

3. In a nozzle having an exit orifice, a normally open passage leadingfrom the intake end of said nozzle to such orifice, a plurality ofnormally closed passages leading from the intake end of said nozzle tosuch orifice, an exit valve member normally closing such orificeexternally thereof, a regulating valve member operative sequentially toopen said normally closed passages in response to increase in fluidintake pressure, means connecting said exit valve member and regulatingValve member for reciprocation in unison, and resilient means urgingsaid exit valve member to closed position thereby likewise to close saidnormally closed passages, said exit valve member being arranged uponreciprocation to open such exit orifice before said regulating valveopens the first of said normally closed passages.

4. In a nozzle having an exit orifice, an exit valve member normallyclosing such orice externally thereof, a plurality of passages leadingfrom the intake end of said nozzle to such orifice, a regulating valvemember mounted for reciprocation toward such exit orifice in response toiiuid intake pressure sequentially to open said passages to permitincreasing flow of fluid to such orifice, and means connecting saidregulating valve member and exit valve member for reciprocation inunison to control the position of said exit valve member relative to therate of fluid flow.

5. In a nozzle having an exit orifice, a swirl chamber immediatelyupstream of such orifice, an exit valve member normally closing suchorifice externally thereof, a small passage leading from the intake endof said nozzle to said swirl chamber including a helical terminalportion adapted to deliver a swirling fiow generally axially of saidchamber, a second larger passage leading from the intake end of saidnozzle to said swirl chamber including a helical terminal portionadapted to deliver a swirling flow generally axially of said chamber, athird still larger passage leading from the intake end of said nozzle tosaid swirl chamber including a terminal portion generally tangential tosaid chamber to deliver a swirling flow thereto, a regulating valvemember upstream of said swirl chamber operative sequentially to opensaid second and third passages by movement toward such exit orifice inresponse to increase in fluid intake pressure, said first small passagebeing normally open, and means connecting said exit valve member andregulating valve member for reciprocation in unison, said exit valvemember being arranged upon reciprocation to open such exit orificebefore said regulating valve opens said second passage.

6. In a nozzle having an exit orifice, a normally open passage leadingfrom the intake end of said nozzle to such orifice, a plurality ofnormally closed passages leading from the intake end of said nozzle tosuch orifice, an exit valve member normally closing such orificeexternally thereof, a regulating valve member operative sequentially toopen said normally closed passages in response to increase in fluidintake pressure, the valved inlet openings of said passages beingclosely adjacent and not more than eight thousandths of an inch apart,and means connecting said exit valve member and regulating valve memberfor reciprocation in unison, said exit valve member being arranged uponreciprocation to open such exit orifice before said regulating valveopens the first of said normally closed passages.

7. In a nozzle having an exit orifice, an exit valve member normallyclosing such orifice externally thereof, a plurality of passages leadingfrom the intake end of said nozzle to such orifice, a regulating valvemember spaced upstream of said orifice mounted for reciprocation inresponse to fluid intake pressure sequentially to open said passages topermit increasing iiow of iiuid to such orifice, the valved inletopenings of said normally closed passages being extremely close togetherfor prompt sequential opening and closing by said regulating valvemember, and means connecting said regulating valve member and exit valvemember for reciprocation in unison to control the position of said exitvalve member relative to the rate of fiuid flow.

8. The nozzle of claim 7, wherein the inlet opening of the first of saidnormally closed passages to be uncovered by said regulating valve memberdoes not exceed eight thousandths of an inch in width longitudinally ofsaid nozzle.

9. In a nozzle having an exit orifice, a swirl chamber immediatelyupstream of such orifice, a small passage leading from the intake end ofsaid nozzle to said swirl chamber including a helical terminal portionadapted to deliver a swirling iiow generally axially of said chamber, asecond larger passage leading from the intake end of said nozzle to saidswirl chamber including a helical terminal portion adapted to deliver aswirling liow generally axially of said chamber, a third still largerpassage leading from the intage end of said nozzle to said swirl chamberincluding a terminal portion generally tangential to said chamber todeliver a swirling flow thereto, and a regulating valve member operativesequentially to open said second and third passages in response toincrease in fluid intake pressure, said rst small passage being normallyopen.

l0. In a nozzle having an exit orifice, a swirl chamber immediatelyupstream of such orifice, a small normally open passage leading from theintake end of said nozzle to said swirl chamber including a helicalterminal portion adapted to deliver a swirling ow to said chamber, aplurality of normally closed passages leading from the intake end ofsaid nozzle to said swirl chamber each of which includes a helicalterminal portion adapted to deliver a swirling flow to said chamber, anda regulating 5 valve member operative sequentially to open said normallyclosed passages in response to increase in uid intake pressure.

References Cited in the le of this patent UNITED STATES PATENTS FOREIGNPATENTS Germany June 14, 1930

